EP1540206B1 - Tensioning mechanism for locked-center idler - Google Patents
Tensioning mechanism for locked-center idler Download PDFInfo
- Publication number
- EP1540206B1 EP1540206B1 EP03764701A EP03764701A EP1540206B1 EP 1540206 B1 EP1540206 B1 EP 1540206B1 EP 03764701 A EP03764701 A EP 03764701A EP 03764701 A EP03764701 A EP 03764701A EP 1540206 B1 EP1540206 B1 EP 1540206B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- adjusting member
- tension adjusting
- locked
- reaction
- dual function
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
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- 238000000034 method Methods 0.000 claims description 4
- 238000004891 communication Methods 0.000 abstract description 2
- 238000013461 design Methods 0.000 description 5
- 238000009434 installation Methods 0.000 description 5
- 238000010276 construction Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 238000013459 approach Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000003213 activating effect Effects 0.000 description 1
- 230000004913 activation Effects 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
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- 239000000314 lubricant Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/08—Means for varying tension of belts, ropes, or chains
- F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
- F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/18—Means for guiding or supporting belts, ropes, or chains
- F16H7/20—Mountings for rollers or pulleys
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
- F16C13/006—Guiding rollers, wheels or the like, formed by or on the outer element of a single bearing or bearing unit, e.g. two adjacent bearings, whose ratio of length to diameter is generally less than one
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C23/00—Bearings for exclusively rotary movement adjustable for aligning or positioning
- F16C23/10—Bearings, parts of which are eccentrically adjustable with respect to each other
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/18—Means for guiding or supporting belts, ropes, or chains
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/63—Gears with belts and pulleys
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/08—Means for varying tension of belts, ropes, or chains
- F16H2007/0842—Mounting or support of tensioner
- F16H2007/0844—Mounting elements essentially within boundaries of final output members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/08—Means for varying tension of belts, ropes, or chains
- F16H2007/0876—Control or adjustment of actuators
- F16H2007/088—Manual adjustment
Definitions
- This invention relates generally to an automatic locked-center idler for tensioning a power transmission belt of a belt drive system. Particularly, this invention relates to an automatic locked-center idler that provides an initial tension setting for a belt drive system. Specifically, this invention relates to such an automatic locked-center idler for a power transmission belt drive system to drive accessories of an internal combustion engine use.
- locked-center idler in conjunction with an accessory belt drive system, for an internal combustion engine, that provides an initial belt tension to remove slack from the belt.
- the installation entails first fastening the idler loosely in place. The installer then forces the idler, including its tensioning member supporting the pulley and the pulley, against the power transmission belt to create substantial tension upon the belt. While holding the idler in this condition, the installer must then tighten the fastener of the idler to fix it in place.
- This installation procedure is fairly strenuous, particularly when performed repeatedly throughout a shift. Further, it is prone to error. The idler can readily be tightened with insufficient tension or no tension placed upon the belt.
- JP-59-083857 discloses a locked center idler according to the preamble of claim 1 and a method for applying tension to a belt drive transmission according to the preamble of claim 5.
- Another version of locked-center idler incorporates a pre-loaded spring. Installation of this version entails fastening the idler firmly in place. Then, activating the pre-loaded spring moves the pulley into tensioning position against the belt. This installation procedure is less strenuous and less prone to error. There is less opportunity for the idler to provide some but insufficient belt tension. However, this procedure still allows an installation where activation of the pre-loaded spring is forgotten. Thus, no initial tension is placed upon the belt. Further, this version of locked-center idler is more complicated in design and construction with the attendant increase in expense to build.
- Prior art locked-center idlers have been limited to being either difficult and error prone to install, or more complicated of design and still relatively error prone to install. Accordingly, there is a continuing need for a locked-center idler that is at once less strenuous to install, less prone to being incorrectly installed, but remains simple in design and construction.
- the object of the invention is achieved by means of a locked center idler according to claim 1 and a method of applying tension to a belt drive power transmission system according to claim 5.
- the invention is an improved locked-center idler of the type having a pulley supported by a bearing.
- the bearing is mounted upon a tension adjusting member. It is improved by the tension adjusting member being in communication with a dual function fastener.
- Figures 1 and 2 depict a preferred embodiment of automatic locked-center idler 10. It includes tensioning member 12 as a tension adjusting member having main cylindrical portion 14 which supports bearing 16.
- the bearing 16 depicted is of the most commonly used type for such applications, a ball bearing. However, other bearing types may be appropriate.
- Pulley 18 is mounted upon bearing 16 in common fashion.
- Tensioning member 12 further includes secondary cylindrical portion 20 having eccentric bore 22 running axially there through and through main cylindrical portion 14. Extending radially above main cylindrical portion is ledge 23 having reaction friction surface 25. Under secondary cylindrical portion 20 is resistance friction surface 27.
- Locked-center idler 10 also includes dual function fastener 24.
- Dual function fastener 24 has shaft 26, upon which are threads 28.
- Dual function fastener also includes head 30 which is depicted as hexagonal. However, any appropriate head shape is contemplated.
- Extending radially from shaft 28 and adjacent to head 30 is flange 32.
- Flange 32 further includes reaction mating surface 34 and annular recess 36.
- the average radius of the contact of reaction mating surface 34 upon reaction friction surface 25 is defined as reaction radius R1.
- the average radius of the contact of resistance friction surface 27 upon mount 38 is defined as R2.
- automatic locked-center idler 10 is assembled as depicted in Figures 1 and 2.
- Automatic locked-center idler 10 is placed upon mount 38.
- Mount 38 can be the cylinder block of an internal combustion engine or a separate structure that is immobile in reference to the cylinder block.
- Power transmission belt 40 is trained about pulley 18.
- Dual function fastener 24 is threaded into mating threads (not depicted) of mount 38.
- Dual function fastener 24 is tightened. As dual function fastener 24 is tightened: 1) tensioning member 12 is clamped between mount 38 and reaction mating surface 34; and, 2) flange 32 and reaction mating surface 34 rotate.
- reaction torque is greater than the torque generated by the resistance friction between resistance friction surface 27 and mounting surface 42 of mount 38, the resistance torque.
- These relative torques can be accomplished in a number of ways.
- One group of ways is to control the relative coefficients of friction of the reaction friction and the resistance friction.
- this can be done by selection of dissimilar materials. For example, if dual function fastener 24 and tension adjusting member 12 are common steel while mount 38 is aluminum, then the static coefficient of friction giving rise to the reaction friction will be relatively large, approximately .7; the static coefficient of friction giving rise to the resistance friction will be relatively small, approximately .45. However, the dynamic coefficients of friction are much closer together. Further, there can be many overriding factors that may limit which materials are available for this application. Accordingly, selection of materials may not always be available as an effective approach.
- Another example of controlling relative coefficients of friction is interjecting a lubricant to reduce resistance friction. Further, various coatings can be applied to surfaces 25, 27, 34, or 42 to modify relative coefficients of friction. Additionally, surfaces 25, 27, 34, or 42 can be textured to modify relative coefficients of friction.
- Annular recess 36 allows greater control over the point at which tensioning member 12 no longer rotates in response to belt tension. It both makes the mating area of reaction friction surface 25 and reaction mating surface 34 more consistent during tightening of dual function fastener 24 and allows give in flange 32 so that the point at which automatic locked-center idler is adequately fixed to mount 38 is less critical.
- reaction torque is the result of torque generated by the reaction friction between reaction friction surface 25 and reaction mating surface 34 multiplied by radius R1 when dual function fastener 24 is placed into dual function fastener receiving bore 52 and tightened.
- resistance torque is the result of torque generated by the resistance friction between resistance friction surface 27 and mounting surface 42 of mount 38 multiplied by radius R2.
- This configuration cannot be expected to produce as much tension on belt 40 is can the prior embodiment.
- the amount of pressure idler 10 can place upon belt 40 is the torque placed upon tension member 12 divided by the length of the lever arm defined by the distance from the center of dual function fastener to the center of pulley 18.
- the lever arm of the prior embodiment is much shorter than the lever arm of the current embodiment.
- the construction of this embodiment has the advantage that tensioning member 12 is of a plainer design and applicable to certain engine and power transmission drive geometries.
- securing bolt 44 operating within securing slot 46 may be necessary to stabilize the tension supplied by automatic locked-center idler 10.
- FIG. 5 and 6 operates similarly to the embodiment of Figures 1 and 2 and utilizes the same principle of rotating tensioning member 12 by the difference of reaction torque to resistance torque. A substantial difference lies in the point about which tensioning member 12 pivots.
- tensioning member 12 pivots about dual function fastener 24.
- tensioning member 12 pivots about pivot 48 extending axially from resistance friction surface 14.
- eccentric bore 22 is replaced by tensioning slot 50.
- reaction torque is the result of torque generated by the reaction friction between reaction friction surface 25 and reaction mating surface 34.
- resistance torque is the result of torque generated by the resistance friction between resistance friction surface 27 and mounting surface 42 of mount 38.
Abstract
Description
- This invention relates generally to an automatic locked-center idler for tensioning a power transmission belt of a belt drive system. Particularly, this invention relates to an automatic locked-center idler that provides an initial tension setting for a belt drive system. Specifically, this invention relates to such an automatic locked-center idler for a power transmission belt drive system to drive accessories of an internal combustion engine use.
- It is known to use a locked-center idler in conjunction with an accessory belt drive system, for an internal combustion engine, that provides an initial belt tension to remove slack from the belt. For one version of locked-center idler, the installation entails first fastening the idler loosely in place. The installer then forces the idler, including its tensioning member supporting the pulley and the pulley, against the power transmission belt to create substantial tension upon the belt. While holding the idler in this condition, the installer must then tighten the fastener of the idler to fix it in place. This installation procedure is fairly strenuous, particularly when performed repeatedly throughout a shift. Further, it is prone to error. The idler can readily be tightened with insufficient tension or no tension placed upon the belt.
- JP-59-083857 discloses a locked center idler according to the preamble of claim 1 and a method for applying tension to a belt drive transmission according to the preamble of claim 5.
- Another version of locked-center idler incorporates a pre-loaded spring. Installation of this version entails fastening the idler firmly in place. Then, activating the pre-loaded spring moves the pulley into tensioning position against the belt. This installation procedure is less strenuous and less prone to error. There is less opportunity for the idler to provide some but insufficient belt tension. However, this procedure still allows an installation where activation of the pre-loaded spring is forgotten. Thus, no initial tension is placed upon the belt. Further, this version of locked-center idler is more complicated in design and construction with the attendant increase in expense to build.
- Prior art locked-center idlers have been limited to being either difficult and error prone to install, or more complicated of design and still relatively error prone to install. Accordingly, there is a continuing need for a locked-center idler that is at once less strenuous to install, less prone to being incorrectly installed, but remains simple in design and construction.
- The object of the invention is achieved by means of a locked center idler according to claim 1 and a method of applying tension to a belt drive power transmission system according to claim 5.
- An automatic locked-center idler is disclosed herein. The invention is an improved locked-center idler of the type having a pulley supported by a bearing. The bearing is mounted upon a tension adjusting member. It is improved by the tension adjusting member being in communication with a dual function fastener.
- The accompanying drawings, which are incorporated in and form part of the specification in which like numerals designate like parts, illustrate preferred embodiments of the present invention and together with the description, serve to explain the principles of the invention. In the drawings:
- Figure 1 is a plan view of a preferred embodiment of an automatic locked-center idler;
- Figure 2 is a section of the preferred embodiment of an automatic locked-center idler depicted in Figure 2 taken along line 2-2;
- Figure 3 is a plan view of a preferred embodiment of an automatic locked-center idler;
- Figure 4 is a section of the preferred embodiment of an automatic locked-center idler depicted in Figure 3 taken along line 4-4;
- Figure 5 is a plan view of a preferred embodiment of an automatic locked-center idler; and,
- Figure 6 is a section of the preferred embodiment of an automatic locked-center idler depicted in Figure 5 taken along line 6-6;
- Figures 1 and 2 depict a preferred embodiment of automatic locked-
center idler 10. It includes tensioningmember 12 as a tension adjusting member having maincylindrical portion 14 which supports bearing 16. Thebearing 16 depicted is of the most commonly used type for such applications, a ball bearing. However, other bearing types may be appropriate. Pulley 18 is mounted upon bearing 16 in common fashion. Tensioningmember 12 further includes secondarycylindrical portion 20 havingeccentric bore 22 running axially there through and through maincylindrical portion 14. Extending radially above main cylindrical portion is ledge 23 havingreaction friction surface 25. Under secondarycylindrical portion 20 isresistance friction surface 27. - Locked-
center idler 10 also includesdual function fastener 24.Dual function fastener 24 hasshaft 26, upon which arethreads 28. Dual function fastener also includeshead 30 which is depicted as hexagonal. However, any appropriate head shape is contemplated. Extending radially fromshaft 28 and adjacent tohead 30 isflange 32.Flange 32 further includesreaction mating surface 34 andannular recess 36. The average radius of the contact ofreaction mating surface 34 uponreaction friction surface 25 is defined as reaction radius R1. The average radius of the contact ofresistance friction surface 27 uponmount 38 is defined as R2. - In practice, automatic locked-
center idler 10 is assembled as depicted in Figures 1 and 2. Automatic locked-center idler 10 is placed uponmount 38. Mount 38 can be the cylinder block of an internal combustion engine or a separate structure that is immobile in reference to the cylinder block.Power transmission belt 40 is trained aboutpulley 18.Dual function fastener 24 is threaded into mating threads (not depicted) ofmount 38.Dual function fastener 24 is tightened. Asdual function fastener 24 is tightened: 1)tensioning member 12 is clamped betweenmount 38 andreaction mating surface 34; and, 2)flange 32 andreaction mating surface 34 rotate. - It is fundamental that the torque generated by the reaction friction between
reaction friction surface 25 andreaction mating surface 34, the reaction torque, is greater than the torque generated by the resistance friction betweenresistance friction surface 27 and mountingsurface 42 ofmount 38, the resistance torque. - These relative torques can be accomplished in a number of ways. One group of ways is to control the relative coefficients of friction of the reaction friction and the resistance friction. By way of example, this can be done by selection of dissimilar materials. For example, if
dual function fastener 24 andtension adjusting member 12 are common steel whilemount 38 is aluminum, then the static coefficient of friction giving rise to the reaction friction will be relatively large, approximately .7; the static coefficient of friction giving rise to the resistance friction will be relatively small, approximately .45. However, the dynamic coefficients of friction are much closer together. Further, there can be many overriding factors that may limit which materials are available for this application. Accordingly, selection of materials may not always be available as an effective approach. Another example of controlling relative coefficients of friction is interjecting a lubricant to reduce resistance friction. Further, various coatings can be applied tosurfaces - Another approach to controlling relative torques is to control the lever arms acted upon by the reaction friction and the resistance friction. As is apparent, the axial force delivered to all
surfaces surfaces resistance friction surface 27 will slide against mountingsurface 42 first, causing resistance torque to drop suddenly as the associated coefficient of friction drops suddenly in going from static to dynamic. - In the embodiment depicted in Figures 1 and 2, with radius R1 larger than radius R2, as
dual function fastener 24 is tightened, tensioningmember 12 is rotated. Because of the placement ofeccentric bore 22, tighteningmember 12 andpulley 18 move towardbelt 40. This leads to a longer path forbelt 40 and tightening ofbelt 40. Oncebelt 40 reaches a certain degree of tension, the reaction torque minus the resistance torque will no longer be enough to continue to rotate tighteningmember 12 and slippage will occur betweenreaction friction surface 25 andreaction mating surface 34. Sometime after this point, dual function fastener is no longer tightened.Belt 40 will have been tightened to the desire setting. Also, automatic locked-center idler will have been affixed to mount 38. The ratio of radius R1 and radius R2 can be chosen to either produce a tension onbelt 40 merely enough to remove the slack from the belt or any other operating amount. - Optional
annular recess 36 is depicted in this embodiment.Annular recess 36 allows greater control over the point at which tensioningmember 12 no longer rotates in response to belt tension. It both makes the mating area ofreaction friction surface 25 andreaction mating surface 34 more consistent during tightening ofdual function fastener 24 and allows give inflange 32 so that the point at which automatic locked-center idler is adequately fixed to mount 38 is less critical. - The embodiment of Figures 3 and 4 utilizes the same principle of rotating tensioning
member 12 by the difference of reaction torque to resistance torque. However, tensioningmember 12 is reformed in the shape of the plate depicted in Figures 3 and 4. Tensioningmember 12 also includes all necessary remaining structure to supportbearing 16 andpulley 18. As with the prior embodiment, reaction torque is the result of torque generated by the reaction friction betweenreaction friction surface 25 andreaction mating surface 34 multiplied by radius R1 whendual function fastener 24 is placed into dual function fastener receiving bore 52 and tightened. Likewise, resistance torque is the result of torque generated by the resistance friction betweenresistance friction surface 27 and mountingsurface 42 ofmount 38 multiplied by radius R2. - This configuration cannot be expected to produce as much tension on
belt 40 is can the prior embodiment. The amount of pressure idler 10 can place uponbelt 40 is the torque placed upontension member 12 divided by the length of the lever arm defined by the distance from the center of dual function fastener to the center ofpulley 18. As can be seen, the lever arm of the prior embodiment is much shorter than the lever arm of the current embodiment. However, the construction of this embodiment has the advantage that tensioningmember 12 is of a plainer design and applicable to certain engine and power transmission drive geometries. - It is contemplated that for those belt drive power transmission systems that operate under high tensions, securing
bolt 44 operating within securingslot 46 may be necessary to stabilize the tension supplied by automatic locked-center idler 10. - The embodiment of Figures 5 and 6 operates similarly to the embodiment of Figures 1 and 2 and utilizes the same principle of rotating tensioning
member 12 by the difference of reaction torque to resistance torque. A substantial difference lies in the point about which tensioningmember 12 pivots. In the first embodiment, tensioningmember 12 pivots aboutdual function fastener 24. In the current embodiment, tensioningmember 12 pivots aboutpivot 48 extending axially fromresistance friction surface 14. To accommodate the different pivot point,eccentric bore 22 is replaced by tensioningslot 50. - As with the prior embodiments, reaction torque is the result of torque generated by the reaction friction between
reaction friction surface 25 andreaction mating surface 34. Likewise, resistance torque is the result of torque generated by the resistance friction betweenresistance friction surface 27 and mountingsurface 42 ofmount 38. - In sum, the preferred embodiments described herein and depicted in the Figures allow an automatic locked-center idler of simple design and construction that is installable without being unduely strenuous or error prone..
- The foregoing description and illustrative embodiments of the present invention have been shown on the drawings and described in detail in varying modifications and alternative embodiments. It should be understood, however, that the foregoing description of the invention is exemplary only, and that the scope of the invention is to be limited only to the claims as interpreted in view of the prior art.
Claims (5)
- A locked-center idler (10) comprising:a pulley (18) supported by a bearing (16) said bearing (16) mounted upon a tension adjusting member (12) that is itself mounted on a mounting surface (42) about a pivot axis eccentric to the pulley, by means of a dual function fastener (24);characterized in that said tension adjusting member (12) comprises a reaction friction surface (25) and a resistance friction surface (27) and the dual function fastener comprises a reaction mating surface (34); and
wherein said reaction friction surface (25) operates with the reaction mating surface (34) to produce a reaction torque upon said tension adjusting member (12) greater than a resistance torque produced by a cooperation of said resistance friction surface (27) with said mounting surface (42) when said dual function fastener (24) is tightened, thus causing said tension adjusting member (12) to rotate about its pivot axis until restrained by increased tension in a power transmission belt (40) entrained about said pulley (18) and thereafter fixing the position of the tension adjusting member (12). - The locked-center idler of claim 1 wherein said tension adjusting member (12) comprises a cylindrical portion (14) adapted to cooperate with an inner portion of a bearing (16) and an eccentric bore (22) axially there through.
- The locked-center idler of claim 1 wherein said tension adjusting member (12) comprises an arm with a pulley mounting portion and a dual function fastener, receiving bore.
- The locked-center idler of claim 1 wherein said tension adjusting member (12), comprises a cylindrical portion (14) adapted to cooperate with an inner portion of a bearing (16), a pivot (48) extending axially and offset from the center of said cylindrical portion (14), a curved slot opening through the length of said cylindrical portion (14) and having a mean curvature with an arc that defines a radius about said pivot (48).
- A method of applying tension to a belt drive power transmission system, characterized by:providing a locked center idler (10) according to claim 1;attaching said tension adjusting member (12) upon a mount that is substantially immobile in relation to an engine cylinder block with a dual function fastener (24);training a power transmission belt (40) about said pulley assembly (18); andapplying a tightening torque to said dual function fastener (24), thereby applying tension to said power transmission belt and fixing the position of said tension adjusting member (12).
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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US39577302P | 2002-07-11 | 2002-07-11 | |
US395773P | 2002-07-11 | ||
PCT/US2003/022139 WO2004008000A1 (en) | 2002-07-11 | 2003-07-10 | Tensioning mechanism for locked-center idler |
Publications (2)
Publication Number | Publication Date |
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EP1540206A1 EP1540206A1 (en) | 2005-06-15 |
EP1540206B1 true EP1540206B1 (en) | 2007-01-03 |
Family
ID=30115925
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP03764701A Expired - Lifetime EP1540206B1 (en) | 2002-07-11 | 2003-07-10 | Tensioning mechanism for locked-center idler |
Country Status (15)
Country | Link |
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US (1) | US20040009837A1 (en) |
EP (1) | EP1540206B1 (en) |
JP (1) | JP2005530972A (en) |
KR (1) | KR100857867B1 (en) |
CN (1) | CN1666039A (en) |
AT (1) | ATE350605T1 (en) |
AU (1) | AU2003256553B2 (en) |
BR (1) | BR0312556A (en) |
CA (1) | CA2492684A1 (en) |
DE (1) | DE60310959T2 (en) |
ES (1) | ES2278200T3 (en) |
MX (1) | MXPA05001562A (en) |
PL (1) | PL376717A1 (en) |
TW (1) | TWI223037B (en) |
WO (1) | WO2004008000A1 (en) |
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WO2005043002A2 (en) * | 2003-10-28 | 2005-05-12 | Patriot Universal Holdings, Llc. | System for belt tensioning and food product molding |
US7824286B2 (en) * | 2005-03-28 | 2010-11-02 | York Industries, Inc. | Device for placing a looped belt under tension |
DE102008035204B3 (en) * | 2008-07-28 | 2010-01-21 | Ab Skf | role |
US8091629B2 (en) * | 2009-06-16 | 2012-01-10 | Weatherford/Lamb, Inc. | Adjustable wireline sheave for stuffing box |
US8210502B2 (en) * | 2009-06-16 | 2012-07-03 | Weatherford/Lamb, Inc. | Adjustable wireline sheave for hay pulley |
CN101968107A (en) * | 2010-09-03 | 2011-02-09 | 重庆长安汽车股份有限公司 | Idler assembly of high-sealing engine accessory gear train |
EP2478984B1 (en) * | 2011-01-20 | 2015-03-25 | Makita Corporation | Motorised work device with a tensioning device for a belt |
FR2970755B1 (en) * | 2011-01-24 | 2015-09-11 | Skf Ab | BELT TENSION ROLLER DEVICE AND ASSOCIATED ASSEMBLY METHOD |
CN103982609A (en) * | 2014-05-08 | 2014-08-13 | 东风商用车有限公司 | Eccentric idler and use method thereof |
CN105909736A (en) * | 2016-06-01 | 2016-08-31 | 中国建材国际工程集团有限公司 | Synchronous belt tensioning device |
US10495194B2 (en) * | 2017-05-04 | 2019-12-03 | Ford Global Technologies, Llc | Adjustable bracket to adjust front end accessory drive for use with stretch fit belt |
CN109595325B (en) * | 2019-01-17 | 2024-03-15 | 中国恩菲工程技术有限公司 | Friction power take-off wheel |
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---|---|---|---|---|
FR2323913A1 (en) * | 1975-09-11 | 1977-04-08 | Peugeot | LIMITLESS FORCE STRENGTHENING DEVICE, ESPECIALLY FOR BELT TENSIONER |
DE3043287C2 (en) * | 1979-12-12 | 1985-12-05 | Nippon Seiko K.K., Tokio/Tokyo | Device for tensioning a transmission traction device |
JPS56124426A (en) * | 1980-03-07 | 1981-09-30 | Nissan Eng Kk | Wet type deodorizing method including regeneration process of oxidizing agent |
FR2495721A1 (en) * | 1980-12-08 | 1982-06-11 | Peugeot | METHOD AND DEVICE FOR TENSIONING A TRANSMISSION BELT |
DE3214231C2 (en) * | 1982-04-17 | 1985-12-19 | SKF GmbH, 8720 Schweinfurt | Tension pulley for belt drives |
JPS5983857A (en) * | 1982-11-02 | 1984-05-15 | Koyo Seiko Co Ltd | Timing belt tensioner |
SU1295098A1 (en) * | 1985-06-11 | 1987-03-07 | Проектно-Конструкторский Технологический Институт Всесоюзного Промышленного Объединения Союзуглемаша Министерства Угольной Промышленности Ссср | Device for tightening flexible members |
JPS62151657A (en) * | 1985-12-25 | 1987-07-06 | Koyo Seiko Co Ltd | Belt tension adjusting device |
US4767383A (en) * | 1986-11-03 | 1988-08-30 | St John Richard C | Adjustable tensioner for belt and chain drives |
DE3906787A1 (en) * | 1989-03-03 | 1990-09-13 | Muhr & Bender | Mechanical stressing device |
JPH0417059A (en) | 1990-05-10 | 1992-01-21 | Canon Inc | Document preparing device |
DE19634343C2 (en) * | 1996-08-24 | 2003-01-02 | Daimler Chrysler Ag | Clamping device for traction means with fixed clamping path |
JPH10267094A (en) * | 1997-03-25 | 1998-10-06 | Ntn Corp | Tension adjusting device for belt |
EP1062438B1 (en) * | 1998-03-13 | 2002-05-29 | Litens Automotive Partnership | Belt tensioner for motor vehicle |
DE69903842T2 (en) * | 1998-09-18 | 2003-09-18 | Litens Automotive Inc | BELT TENSIONER AND METHOD FOR ITS INSTALLATION |
-
2003
- 2003-07-10 CN CN038162628A patent/CN1666039A/en active Pending
- 2003-07-10 JP JP2004521869A patent/JP2005530972A/en active Pending
- 2003-07-10 US US10/617,628 patent/US20040009837A1/en not_active Abandoned
- 2003-07-10 KR KR1020057000465A patent/KR100857867B1/en not_active IP Right Cessation
- 2003-07-10 CA CA002492684A patent/CA2492684A1/en not_active Abandoned
- 2003-07-10 EP EP03764701A patent/EP1540206B1/en not_active Expired - Lifetime
- 2003-07-10 DE DE60310959T patent/DE60310959T2/en not_active Expired - Fee Related
- 2003-07-10 MX MXPA05001562A patent/MXPA05001562A/en active IP Right Grant
- 2003-07-10 BR BR0312556-4A patent/BR0312556A/en not_active IP Right Cessation
- 2003-07-10 ES ES03764701T patent/ES2278200T3/en not_active Expired - Lifetime
- 2003-07-10 PL PL376717A patent/PL376717A1/en unknown
- 2003-07-10 WO PCT/US2003/022139 patent/WO2004008000A1/en active IP Right Grant
- 2003-07-10 AU AU2003256553A patent/AU2003256553B2/en not_active Ceased
- 2003-07-10 AT AT03764701T patent/ATE350605T1/en not_active IP Right Cessation
- 2003-07-11 TW TW092118980A patent/TWI223037B/en not_active IP Right Cessation
Also Published As
Publication number | Publication date |
---|---|
EP1540206A1 (en) | 2005-06-15 |
ES2278200T3 (en) | 2007-08-01 |
AU2003256553B2 (en) | 2007-11-08 |
DE60310959D1 (en) | 2007-02-15 |
AU2003256553A1 (en) | 2004-02-02 |
TW200405927A (en) | 2004-04-16 |
WO2004008000A1 (en) | 2004-01-22 |
KR20050025338A (en) | 2005-03-14 |
JP2005530972A (en) | 2005-10-13 |
DE60310959T2 (en) | 2007-11-15 |
CA2492684A1 (en) | 2004-01-22 |
TWI223037B (en) | 2004-11-01 |
ATE350605T1 (en) | 2007-01-15 |
CN1666039A (en) | 2005-09-07 |
BR0312556A (en) | 2005-10-18 |
US20040009837A1 (en) | 2004-01-15 |
MXPA05001562A (en) | 2005-04-25 |
KR100857867B1 (en) | 2008-09-10 |
PL376717A1 (en) | 2006-01-09 |
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